EP0187891A2 - Bague d'étanchéité à lèvre - Google Patents

Bague d'étanchéité à lèvre Download PDF

Info

Publication number
EP0187891A2
EP0187891A2 EP85107716A EP85107716A EP0187891A2 EP 0187891 A2 EP0187891 A2 EP 0187891A2 EP 85107716 A EP85107716 A EP 85107716A EP 85107716 A EP85107716 A EP 85107716A EP 0187891 A2 EP0187891 A2 EP 0187891A2
Authority
EP
European Patent Office
Prior art keywords
shaft
disc
thickness
sealing
stiffening ring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP85107716A
Other languages
German (de)
English (en)
Other versions
EP0187891A3 (en
EP0187891B1 (fr
Inventor
Dieter Fuchs
Wolfgang Schmitt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carl Freudenberg KG
Original Assignee
Carl Freudenberg KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carl Freudenberg KG filed Critical Carl Freudenberg KG
Priority to AT85107716T priority Critical patent/ATE58422T1/de
Publication of EP0187891A2 publication Critical patent/EP0187891A2/fr
Publication of EP0187891A3 publication Critical patent/EP0187891A3/de
Application granted granted Critical
Publication of EP0187891B1 publication Critical patent/EP0187891B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3228—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip formed by deforming a flat ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/04—PTFE [PolyTetraFluorEthylene]
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S277/00—Seal for a joint or juncture
    • Y10S277/922—Bonding or joining for manufacture of seal

Definitions

  • the invention relates to a radial shaft sealing ring, comprising a sealing element made of a non-elastomeric plastic, preferably made of PTFE, which is produced from a flat disk with plane-parallel surfaces and which is fixed in the area of its outer circumference in a stiffening ring and is bulged cold in the axial direction in the area of its inner circumference and under a prestress abuts the shaft.
  • a sealing element made of a non-elastomeric plastic, preferably made of PTFE, which is produced from a flat disk with plane-parallel surfaces and which is fixed in the area of its outer circumference in a stiffening ring and is bulged cold in the axial direction in the area of its inner circumference and under a prestress abuts the shaft.
  • DE-OS 25 53 290 refers to a radial shaft sealing ring of the aforementioned type.
  • This contains a sealing element produced from a flat disc. This is bulged in the area of its inner circumference to form a cylindrical end section in the direction of the sealed space and has in the area contacting the shaft to be sealed, relief-like projecting return ribs for the case drain fluid on. For this reason, achieving a good sealing result depends on the shaft rotating at the correct speed. If the rotational speed of the shaft is too high, this results in an increase in the conveying effect of the ribs, and in addition to insufficient lubrication in the area of the dynamic sealing zone, dust can be conveyed from the environment into the dynamic sealing zone and, if necessary. come into the sealed room. Both are undesirable and can cause the seal to fail prematurely.
  • the conveying effect caused by the ribs also decreases in the direction of the sealed space.
  • the sealed medium in particular in the area of the interstices of the individual ribs, can pass through the dynamic sealing zone in the direction of the outside and lead to contamination here. This effect can be clearly observed and is undesirable, particularly when the shaft is at a standstill and in cases where pressure can build up in the sealed space.
  • the invention has for its object to develop a radial shaft seal of the type mentioned in such a way that the occurrence of the disadvantages mentioned is avoided.
  • the proposed radial shaft sealing ring should always allow a good sealing result regardless of whether the sealed shaft is at a standstill or rotating, even when the pressure changes direction. is good for sealing the crankshaft Two-stroke engine are suitable.
  • a radial shaft sealing ring of the type mentioned is proposed according to the invention, which is characterized in that the disk has a thickness of 0.3-0.8 mm and an inside diameter which is about 1.5 in relation to the diameter of the shaft - 7 times the value of its thickness is reduced and that the distance of the stiffening ring from the shaft at the clamping point of the disk is 2-7 times as large as that
  • the disk preferably has an inner diameter which is reduced by 3-4 times its thickness compared to the diameter of the shaft, the distance of the stiffening ring from the shaft at the clamping point the disc is 3-4 times the thickness of the disc.
  • the sealing element of the radial shaft sealing ring proposed according to the invention is dimensioned considerably smaller and more compact than the design according to the prior art described at the outset, which is, however, completely sufficient with regard to the radial displacements of the shaft to be sealed that occur in normal mechanical engineering.
  • shafts with a diameter in the range between 10 and 40 mm can be sealed off excellently using the radial shaft sealing ring according to the invention.
  • the axial extent of the dynamically sealed zone is dimensioned extremely short, which favors the guarantee of the necessary lubrication by the medium to be sealed in this critical area.
  • the disk Before the sealing ring is installed, the disk can be conically bulged in the axial direction in the region of its inner circumference, for example with the aid of a molding tool.
  • a Heating of the material is avoided in this molding process in order not to impair the reforming efforts of the material used. This ensures that the end section of the disk is pressed uniformly against the surface of the sealed shaft over long periods of time. Even during normal operation, it is not impaired insofar as the small axial expansion of the dynamic sealing zone and its good lubrication preclude excessive heating from the outset.
  • the disk In the region of its end section deformed in the axial direction, the disk has no hydrodynamically acting return conveying elements facing the surface of the sealed shaft.
  • the disk and the sealing axis enclose approximately a right angle in the area enclosed by the stiffening ring.
  • Other mutual assignments are readily possible, but particularly good durability and a good sealing result are achieved with a right-angled assignment.
  • the stiffening ring can have an annular projection on the side of the disk facing away from the bulge, which is extended to the immediate vicinity of the shaft.
  • the axial support of the end section effecting the dynamic seal is thereby improved, with the side effect that there is the advantage that it is difficult to apply dust and dirt to the dynamic seal zone from the outside.
  • the sealing result is also improved. This should be due to the fact that the operational pressure pulsations in this case by the ring projection of the Ver stiffening ring are kept essentially away from the dynamic sealing zone. Best results are achieved in particular in cases where the ring projection of the stiffening ring of the shaft is approximated to a close distance.
  • the inside of the ring projection is expediently delimited by a cylindrical surface, the axial length of which is at least as large as its distance from the shaft, expediently at least 3 times and at most 10 times as large.
  • the stiffening ring is made of plastic and is molded directly onto the pane in the area of the outer circumference.
  • Thermoset materials are preferred. Problems with regard to the mutual fixing and sealing of the two parts can be reliably prevented in this way if the procedure described in DE-PS 33 29 386 is followed.
  • the embodiment shown relates to a seal for use on the crankshaft of a two-stroke engine.
  • This consists of the reinforcement ring 1 and the disc 2.
  • the former is made of glass fiber reinforced phenolic resin and molded directly onto the outer periphery of the disc 2.
  • the washer is thereby insoluble and liquid-tight in the stiffening ring. It encloses a right angle in the area of the definition zone with the sealing axis.
  • the disc which is made of PTFE, is bulged in the direction of the side facing away from the sealed space and lies against the surface of the sealed shaft with a sealing edge which is delimited on both sides by conical surfaces.
  • the washer used has an outer diameter of 27 mm, an inner diameter of 18.2 mm and a thickness of 0.5 mm.
  • the axial extent of the contact surface between the washer and the surface of the sealed shaft that results after installation is approximately 0.3 mm and is therefore extremely short.
  • the radial shaft seal is inexpensive to manufacture and easy to install. When used on the crankshaft of a two-stroke engine, it guarantees an excellent sealing result throughout its entire service life.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Sealing Devices (AREA)
  • Mechanical Sealing (AREA)
  • Glass Compositions (AREA)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
  • Catching Or Destruction (AREA)
  • Finger-Pressure Massage (AREA)
  • Hybrid Cells (AREA)
  • Materials For Medical Uses (AREA)
EP85107716A 1985-01-15 1985-06-21 Bague d'étanchéité à lèvre Expired - Lifetime EP0187891B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85107716T ATE58422T1 (de) 1985-01-15 1985-06-21 Radialwellendichtring.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853501066 DE3501066A1 (de) 1985-01-15 1985-01-15 Radialwellendichtring
DE3501066 1985-01-15

Publications (3)

Publication Number Publication Date
EP0187891A2 true EP0187891A2 (fr) 1986-07-23
EP0187891A3 EP0187891A3 (en) 1988-03-23
EP0187891B1 EP0187891B1 (fr) 1990-11-14

Family

ID=6259841

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85107716A Expired - Lifetime EP0187891B1 (fr) 1985-01-15 1985-06-21 Bague d'étanchéité à lèvre

Country Status (10)

Country Link
US (1) US4645215A (fr)
EP (1) EP0187891B1 (fr)
JP (1) JPS61167780A (fr)
AT (1) ATE58422T1 (fr)
BR (1) BR8505452A (fr)
CA (1) CA1334763C (fr)
DE (2) DE3501066A1 (fr)
ES (1) ES288310Y (fr)
MX (1) MX161446A (fr)
NO (1) NO852847L (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10393268B2 (en) 2014-03-27 2019-08-27 Saint-Gobain Performance Plastics Corporation Rotary shaft housing and seal

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5152538A (en) * 1988-03-21 1992-10-06 Chicago Rawhide Manufacturing Company, Inc. Composite seal assembly
US4898134A (en) * 1989-02-27 1990-02-06 Outboard Marine Corporation Crankcase seal arrangement for two cycle engine
US5544963A (en) * 1993-11-19 1996-08-13 Koyo Seiko Co., Ltd. Bearing seal assembly with specially dimensioned sealing lip
DE19904416A1 (de) * 1999-02-04 2000-08-24 Mtu Friedrichshafen Gmbh Wellendichtring
DE10028159A1 (de) * 2000-06-07 2001-12-13 Mann & Hummel Filter Ölmodul für eine Brennkraftmaschine
CN100343075C (zh) * 2002-10-01 2007-10-17 Nok株式会社 标记形成方法以及形成标记的成形品
US20070163530A1 (en) * 2006-01-13 2007-07-19 Luchs Berndt L Seal assembly
DE102015213221A1 (de) * 2015-07-15 2017-01-19 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids
DE102016225551A1 (de) * 2016-12-20 2018-06-21 Herbert Hänchen GmbH & Co. KG Dichtring für eine dynamische Berührungsdichtung

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE845584C (de) * 1950-10-14 1952-08-04 Knorr Bremse Gmbh Kolbendichtung, in Sonderheit aus Leder
NL284907A (fr) * 1961-11-01
US3275331A (en) * 1962-12-21 1966-09-27 Johns Manville Seal and method of manufacture
US3511512A (en) * 1968-01-05 1970-05-12 Crane Packing Co Lip seal for light lubricants
DE2229682A1 (de) * 1972-06-19 1974-01-17 Merkel Asbest & Gummiwerke Abstreifer fuer kolbenstangen und dergleichen
US3857156A (en) * 1973-12-19 1974-12-31 Federal Mogul Corp Method of making tetrafluoroethylene sealing elements with hydrodynamic action
US3995868A (en) * 1973-12-20 1976-12-07 The Duriron Company, Inc. Polytetrafluoroethylene lip seal
US4118856A (en) * 1974-12-02 1978-10-10 Garlock Inc Bi-directional hydrodynamic shaft seal method
US4194748A (en) * 1976-01-27 1980-03-25 Firma Carl Freudenberg Radial shaft sealing ring
MX144696A (es) * 1976-08-23 1981-11-11 Dana Corp Mejoras en obturador hidrodinamico de flecha
US4283064A (en) * 1976-08-23 1981-08-11 Dana Corporation Rotary shaft seal
JPS53109062A (en) * 1977-03-03 1978-09-22 Yoshio Arai Oil seal of fluorine resin incorporating elastic body such as spring* and packing or the like* and manufacturing method thereof
JPS56156553A (en) * 1980-05-06 1981-12-03 Hitachi Constr Mach Co Ltd Sealing device for body of revolution
US4350351A (en) * 1980-12-17 1982-09-21 Martin A Eugene Manhole joint gasket assembly and joint formed therewith
GB2105797B (en) * 1981-09-11 1986-01-02 Aerequip Rotary shaft seal
US4451050A (en) * 1981-11-18 1984-05-29 Microdot Inc. Bi-directional hydrodynamic slitted seal
DE3221526C2 (de) * 1982-06-08 1986-03-13 Fa. Carl Freudenberg, 6940 Weinheim Wellendichtring
DE3246152C2 (de) * 1982-12-14 1985-01-03 Fa. Carl Freudenberg, 6940 Weinheim Verfahren zur Herstellung eines Wellendichtringes
US4497496A (en) * 1983-05-16 1985-02-05 Microdot Inc. Hydrodynamic slitted seal and method of manufacture thereof
GB2141797B (en) * 1983-06-09 1987-01-28 Mather Co An annular seal assembly
DE3329386C1 (de) * 1983-08-13 1987-10-01 Fa. Carl Freudenberg, 6940 Weinheim Verfahren zur Herstellung einer Dichtung
DE3402109C2 (de) * 1984-01-21 1987-01-08 Fa. Carl Freudenberg, 6940 Weinheim Dichtung
US4522411A (en) * 1984-10-01 1985-06-11 Chicago Rawhide Mfg. Co. Fluid seals with self-venting auxiliary lips

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10393268B2 (en) 2014-03-27 2019-08-27 Saint-Gobain Performance Plastics Corporation Rotary shaft housing and seal

Also Published As

Publication number Publication date
ATE58422T1 (de) 1990-11-15
US4645215A (en) 1987-02-24
CA1334763C (fr) 1995-03-14
BR8505452A (pt) 1986-12-16
JPH0570757B2 (fr) 1993-10-05
MX161446A (es) 1990-09-27
DE3501066A1 (de) 1986-08-28
DE3501066C2 (fr) 1987-07-09
EP0187891A3 (en) 1988-03-23
NO852847L (no) 1986-07-16
DE3580578D1 (de) 1990-12-20
ES288310Y (es) 1986-09-16
JPS61167780A (ja) 1986-07-29
ES288310U (es) 1986-02-16
EP0187891B1 (fr) 1990-11-14

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